EP2273144B1 - Kurbelwellenentkuppler - Google Patents

Kurbelwellenentkuppler Download PDF

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Publication number
EP2273144B1
EP2273144B1 EP10011294A EP10011294A EP2273144B1 EP 2273144 B1 EP2273144 B1 EP 2273144B1 EP 10011294 A EP10011294 A EP 10011294A EP 10011294 A EP10011294 A EP 10011294A EP 2273144 B1 EP2273144 B1 EP 2273144B1
Authority
EP
European Patent Office
Prior art keywords
decoupler assembly
hub
spring shell
spring
decoupler
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP10011294A
Other languages
English (en)
French (fr)
Other versions
EP2273144A1 (de
Inventor
Bert Mevissen
James W. Dell
John Antchak
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Litens Automotive Partnership
Litens Automotive Inc
Original Assignee
Litens Automotive Partnership
Litens Automotive Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Litens Automotive Partnership, Litens Automotive Inc filed Critical Litens Automotive Partnership
Priority to PL10011294T priority Critical patent/PL2273144T3/pl
Publication of EP2273144A1 publication Critical patent/EP2273144A1/de
Application granted granted Critical
Publication of EP2273144B1 publication Critical patent/EP2273144B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/10—Friction clutches with clutching members co-operating with the periphery of a drum, a wheel-rim, or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/14—Construction providing resilience or vibration-damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/12—Friction clutches with an expansible band or coil co-operating with the inner surface of a drum or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/26—Automatic clutches actuated entirely mechanically acting at definite angular position or disengaging after consecutive definite number of rotations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
    • F16D7/022—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with a helical band or equivalent member co-operating with a cylindrical torque limiting coupling surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys
    • F16H2055/366—Pulleys with means providing resilience or vibration damping

Definitions

  • the invention relates to a crankshaft and drive assembly of an automotive vehicle, and more particularly, to a decoupling assembly that allows the drive assembly to overrun or operate temporarily at a speed different from that of the crankshaft and to decouple or mechanically isolate the drive assembly from the crankshaft and reduce torsional vibrations therebetween.
  • each belt driven accessory component includes a pulley drivingly engaged with the belt and the belt is driven by an output pulley coupled directly to the crankshaft.
  • an internal combustion engine for an automotive vehicle is generally indicated at 10.
  • the engine 10 includes a plurality of belt driven accessory components 12, such as an alternator, compressor, etc.
  • a pulley 14 is operatively coupled to each of the belt driven accessory components 12 for driving the components 12 via rotation of the pulley 14.
  • the engine 10 also includes a crankshaft 16, which generally provides the mechanical torque output resulting from the operation of the engine 10.
  • An endless serpentine belt 18 is seated about each pulley 14 of the belt driven accessory components 12. The belt 18 is driven in a driven direction by the rotation of the crankshaft 16, which causes rotation of the pulleys 14.
  • a crankshaft torque modulator - or decoupler assembly 20 is operatively coupled between the crankshaft 16 and the belt 18.
  • the decoupler assembly 20 is shown in an exploded view and includes an output pulley 22 having an annular outer track 24 defined between a pair of spaced apart, raised and parallel rims 25 that seats the belt 18 therein.
  • the output pulley 22 also includes an annular inner clutch surface 26 opposite and generally concentric with the outer track 24.
  • the output pulley 22 further includes a face plate 28 extending between the outer track 24 and the inner clutch surface 26.
  • a hollow, cylindrical hub 30 projects axially from the center of the face plate 28 concentric with the inner clutch surface 26 for defining a hub bearing surface 32.
  • the decoupler assembly 20 also includes a drive hub 40, preferably formed of metal, fixedly secured to the crankshaft 16 by any suitable fastener or connection means for rotation therewith.
  • the drive hub 40 includes a generally cup-shaped cylindrical main body 42 defining an inner surface 44 and having a circumferential radial rim 45.
  • a bearing post 46 extends axially from the center of the main body 42 to a distal end.
  • At least one, but preferably a plurality of tabs 48, 50 extends radially outwardly radial rim 45 of the main body 42.
  • Each tab 48, 50 includes a leading edge 52 extending generally perpendicularly from the main body 42 and a trailing edge 54 extending angularly from the main body 42.
  • a bearing assembly 60 rotatably couples the output pulley 22 and the drive hub 40.
  • the bearing assembly 60 includes a circular inner race 62 surrounding by a circular outer race 64.
  • a plurality of ball bearings 66 are seated between the inner race 62 and outer race 64.
  • the inner race 62 is seated around the bearing post 46 of the drive hub 40 and the outer race 64 is press fit against the bearing surface 32 of the output pulley 22 to provide the rotatable connection therebetween.
  • the inner race 62 projects axially beyond the outer race 64 to form a shoulder to receive a disc-shaped seal 68 thereon to seal the ball bearings 66 between the inner race 62 and outer race 64 and to seal an oil or grease lubricant within the bearing assembly 60 and output pulley 22, as will be described in further detail herein below.
  • the inner race 62 may be axial flush with the end of the outer race 64.
  • the seal 68 may be seated around an extended collar portion of the bearing post 46 to seal against the ends of both the inner race 62 and outer race 64.
  • the seal 68 may be separate or an integral part of the bearing assembly 60.
  • a bushing can be used instead of the bearing assembly 60. Generally, the bushing would provide greater damping over the bearing assembly 60.
  • the decoupler assembly 20 further includes a lower spring shell 70 and an upper spring shell 100 operatively coupled to the drive hub 40.
  • Each of the shells 70, 100 is preferably molded of an organic plastic material.
  • the lower spring shell 70 is generally disc-shaped and extends between cylindrical and generally concentric inner and outer surfaces 72, 74.
  • a radial rim element 75 projects radially from at least portions of the outer surface 74 forming a shelf or shoulder and outer peripheral bearing surface 77 for frictionally engaging and supporting the inner clutch surface 26 of the output pulley 22.
  • the radial rim element 75 as shown in the preferred embodiment extends only along portions of the periphery of the outer surface to reduce the weight of the lower spring shell 70.
  • the rim element 75 may be a contiguous circumferential rim extending around the entire periphery of the outer surface 74. Further, the radial rim element 75 increases in its axial thickness incrementally and continuously around the circumference of the outer surface 74 to form a helical contour or ramped support surface 79. At least one, but preferably a plurality of trenches 76 is formed and recessed in the lower spring shell 70 between the inner and outer surfaces 72, 74. Each trench 76 extends arcuately between a first end 78 and a second end 80. The trenches 76 are aligned end to end and arranged in a generally circular manner along the perimeter of the lower spring shell 70.
  • a retaining slot 82 extends diagonally between the adjacent ends of the trenches 76 from the outer surface 74 to a generally rectangular cavity 84.
  • An L-shaped or U-shaped blocking tab or clutch stop 85 preferably formed of stamped metal, is seated in the cavity 84.
  • a plurality of cutouts 86 is formed in the outer surface 74 to reduce the weight of the lower spring shell 70 and to form a series of alternating undulations 88, 90 in the outer surface 74. Additionally, a lubricant can be supported in the cutouts 86 for lubricating the inner clutch surface 26 of the output pulley 22.
  • the undulations 88 each include a bore 92 therethrough for receiving a fastener 94, such as a rivet or screw, to fixedly secured the lower spring shell 70 to the upper spring shell 100.
  • the undulations 90 each include an elongated slot 96 for aligning with and engaging with the upper spring shell 100 as will be further described below.
  • the lower spring shell 70 includes an enlarged counter-balance block 98 formed between the inner surface 72 and the outer surface 74 positioned radially opposite the retaining slot 82 and cavity 84 to rotationally balance the lower spring shell 70.
  • the upper spring shell 100 is also generally disc-shaped and extends between cylindrical and generally concentric inner and outer surfaces 102, 104. At least one, but preferably a plurality of trenches 106 is formed and recessed in the upper spring shell 100 between the inner and outer surfaces 102, 104. Each trench 106 extends arcuately between a first end 108 and a second end 110. The trenches 106 are aligned end to end and arranged in a generally circular manner along the perimeter of the upper spring shell 100.
  • a raised blocking wall 112, 114 extends diagonally between each of the pair of adjacent ends of the trenches 106 from the outer surface 102 to the second end 110 of each trench 106 for abutting with the trailing edge 54 of each respective tabs 48, 50 of the drive hub 40. Further, one of the blocking walls 112, 114 is arranged to overlay the clutch stop 85 to retain the stop 85 within the cavity 84 of the lower spring shell 70.
  • the upper spring shell 100 further includes an axially extending alignment tab 115 extending diagonally between the inner surface 102 and outer surface 104. The alignment tab 115 is sized to be received within the retaining slot 82 to ensure correct orientation between the lower and upper spring shells 70, 100.
  • a plurality of cutouts 116 is formed in the outer surface 104 to reduce the weight of the upper spring shell 100 and to form a series of alternating undulations 118, 120 in the outer surface 104. Additionally, a lubricant can be supported in the cutouts 116 for lubricating the inner clutch surface 26 of the output pulley 22.
  • the undulations 118 each include a bore 122 therethrough aligned axial with a corresponding bore 92 in the lower spring shell 70 for receiving the fastener 94 to fixedly secure the lower spring shell 70 to the upper spring shell 100.
  • the undulations 120 each include an axially projecting and slightly tapered tab 124 for aligning axially with a corresponding elongated slot 96 in the lower spring shell 70 and for providing a rigid connection to transmit torque between the lower spring shell 70 and the upper spring shell 100.
  • the upper spring shell 100 includes an enlarged counter-balance block 126 formed between the inner surface 102 and the outer surface 104 positioned radially opposite the retaining slot 82 and cavity 84 in the lower spring shell 70 to rotationally balance the lower and upper spring shells 70, 100.
  • the decoupler assembly 20 also includes a plurality of biasing members 130 in the form of helical coil springs.
  • a biasing member 130 is supported in each of the radially and axially aligned trenches 76; 106 between the lower spring shell 70 and upper spring shell 100.
  • Each biasing member 130 extends arcuately between first and second spring ends 132, 134. Approximately one-half of the first and second spring ends 132, 134 abuts the first and second ends 78, 80 of the trenches 76 in the lower spring shell 70 and the other one-half abuts the first and second ends 108, 110 of the trenches 106 in the upper spring shell 100.
  • the biasing members 130 When the lower and upper spring shells 70, 100 are aligned axially and radially and pressed together, the biasing members 130 are seated in the corresponding trenches 76, 106 between the lower and upper spring shells 70, 100.
  • the biasing members 130 may be preformed in an arcuate shaped corresponding to the arcuate shape of the trenches 76, 106 or may be straight and then bent into shape when seated within the trenches 76, 106. It should also be appreciated that the biasing members 130 may include any compressible or resilient member seated within the trenches 76, 106, such as a rubber strut type member or compressible fluid.
  • a lubricant such as grease or oil
  • the lubricant also enhances damping characteristics of the decoupler assembly 20.
  • the damping characteristics can be tuned for a particular application. That is, the damping characteristics can be decreased or increased, depending on the type of lubricant placed in the trenches 76, 106 and decoupler assembly 20.
  • a clutch element 140 is disposed adjacent the inner clutch surface 26 of the output pulley 22. More specifically, the clutch element 140 is a coil spring having a plurality of coils 142 extending helically between a proximal end 144 and distal end 146. The proximal end 144 of the clutch element 140 is fixedly held in the retaining slot 82 in the lower spring shell 70. The tip of the proximal end 144 of the clutch element 140 extends into the cavity 84 and abuts the clutch stop 85. The clutch element 140 is supported by the radial rim element 75 such that the ramped support surface 79 of the rim element 75 correspondingly mates with the contour of the helical coils 142.
  • the coils 142 are outwardly frictionally engaged with the inner clutch surface 26, such that rotational acceleration of the drive hub 40 relative to the output pulley 22 in the driven direction of the crankshaft 16 causes the coils 142 to expand radially outwardly to couple the drive hub 40 and output pulley 22.
  • the coils 142 grip the inner clutch surface 26 so that the output pulley 22 rotates with the drive hub 40.
  • deceleration of the drive hub 40 relative to the output pulley 22 causes the coils 142 to contract radially inwardly.
  • the coils 142 release grip of the inner clutch surface 26 to allow the output pulley 22 to overrun the drive hub 40.
  • the coils 72 have a rectangular cross section.
  • the decoupler assembly 20 is assembled by seating the biasing members 130 in the trenches 76 of the lower spring shell 70.
  • the clutch stop 85 is placed in the cavity 84.
  • the clutch element 140 is positioned around the lower spring shell 70 and the proximal end 144 is recessed within the retaining slot 82 with the end thereof abutting the clutch stop 85.
  • the clutch element 140 is supported by the radial rim element 75 such that the helical coils 142 mate with the helical contour of the ramped support surface 79 formed by the rim element 75.
  • the drive hub 40 is then positioned in the center of the lower spring shell 70 such that the radial rim 45 is seated against the periphery around the inner surface 72 and the tabs 48, 50 are positioned between the adjacent ends of the trenches 76.
  • the upper spring shell 100 is aligned axially and radially with the lower spring shell 70 such that the biasing members 130 are seated in the trenches 106 and the tabs 48, 50 are similarly positioned between the adjacent ends of the trenches 106.
  • the alignment tab 115 is arranged to be received within the retaining slot 82 to ensure proper orientation between the shells 70, 100 and to position the counter-balance blocks 98, 126 opposite the proximal end 144 of the clutch element 140.
  • the counter-balance block 126 should be arranged generally 180 degrees opposite the proximal end 144 of the clutch element 140.
  • the alignment tab 115 also engages and presses down on the proximal end 144 of the clutch element 140 to retain the end 144 within the retaining slot 82.
  • the upper spring shell 100 is similarly seated within the circumference of the clutch element 140.
  • the axially projecting and tapered tabs 124 are received within the corresponding slots 96 in the lower spring shell 70 to provide a rigid connection and transmit torque between the shells 70, 100.
  • the upper and lower spring shells 70, 100 are fixed connected by passing the fasteners 94 through each of the axially aligned bores 92, 122.
  • the bearing assembly 60 is press fit against the hub bearing surface 32 of the output pulley 22 and the seal 68 is pressed around the inner race 62 against the shoulder formed with the outer race 64 to seal the bearing assembly 60 and output pulley 22.
  • the drive hub 40, lower and upper spring shells 70, 100 and clutch element 140 are then positioned within the annular inner clutch surface 26 with the bearing post 46 of the drive hub 40 extending through the inner race 62 of the bearing assembly 60 to rotatably couple the drive hub 40 and output pulley 22.
  • the clutch element 140 will be in slight frictional engagement with the inner clutch surface 26 and the outer bearing surface 77 of the radial rim element 75 frictionally engages and supports the inner clutch surface 26 of the output pulley 22.
  • the inner cavity of the output pulley 22 is filled with a lubricant, such as grease or oil as desired to reduce friction between the components and provide dampening.
  • a disc-shaped cover plate 150 closes the output pulley 22 and covers the upper spring shell 100.
  • the cover plate 150 includes an inner seal 152 for sealing engagement against the main body 42 of the drive hub 40 and an outer peripheral gasket 154 for sealing against the output pulley 22, together providing a fluid tight sealed decoupler assembly 20.
  • the cover plate 150 may be fixedly secured to the output pulley 22 by roll forming the periphery of a lip 156 on the output pulley 22 against the circumferential outer surface of the cover plate 150.
  • a torsional vibration damper 160 may be fixedly secured to the hub 40 for dampening vibrations experienced at the crankshaft 16 during of the operation of the engine 10.
  • the torsional vibration damper 160 of the preferred embodiment of Figure 9 includes a damper mounting hub 162 mounted to the drive hub 40.
  • An elastomeric ring 164 is secured to the damper mounting hub 162 by an inertia ring 166 to complete the assembly.
  • the engine 10 rotatably accelerates or decelerates the crankshaft 16 and the drive hub 40 in the driven direction V relative to the output pulley 22.
  • the tabs 48, 50 engage the first spring ends 132 of the biasing members 130.
  • the first spring ends 132 are rotatably displaced relative to the respective second spring ends 134 as the biasing members 130 are compressed against the second ends 80, 110 of the trenches 76, 106.
  • the amount of displacement of the second spring ends 134 during acceleration is directly proportional to the rate of acceleration of the drive hub 40 and the stiffness of the biasing members 130.
  • the upper and lower spring shells 70, 100 accelerate with the drive hub 40. That is, the transfer of torque or acceleration from the drive hub 40 to the upper and lower spring shells 70, 100 is slightly delayed during compression of the biasing members 130. Acceleration of the upper and lower spring shells 70, 100 relative to the output pulley 22 causes the coils 142 to expand radially outwardly toward the inner clutch surface 26. More specifically, the rotation of the lower spring shell 70 urges the blocking tab 85 against the proximal end 144 of the clutch element 140 to radially expand the coils 142 against the inner clutch surface 26.
  • the contour of the retaining slot 82 in the lower spring shell 70 supports the proximal end 144 of the clutch element 140 to prevent localized bending of the coils 142 and urge uniform radial expansion along the entire length of the helical coils 142 against the inner clutch surface 26.
  • the coils 142 grip the clutch surface 26 with sufficient friction so that the output pulley 22 rotates with the drive hub 40, driving the belt 18.
  • the decoupler assembly 20 also decouples, dampens and mechanically isolates these torsional vibrations between the crankshaft 16 and the output pulley 20. Specifically, oscillatory torsional vibrations from the crankshaft 16 are dampened or isolated from the output pulley 22 by the biasing members 130. Oscillations of the crankshaft 16, and thus drive hub 40, act on the first ends 132 of the biasing members 130 to compress the biasing members 130 against the second ends 80, 110 of the trenches 76, 106.
  • the biasing members 130 compress and expand continuously with the torsional oscillations of the drive hub 40 to dampen, isolate and absorb the vibration caused by the torsional oscillations.
  • the biasing members 130 thus reduce the impact loads generated within the engine, which would normally be transferred through the' crankshaft 16 and into the output pulley 22, and consequently directly into the belt driven accessory components.
  • the biasing members 130 lower the oscillatory acceleration and deceleration rates and introduce a phase shift between the input force by the drive hub 40 and the output response at the output pulley 22. This phase shift manifest itself as a lowering of the system resonance. By lowering the resonance of the drive assembly, unwanted vibrations are attenuated and torsional displacements induced by a system resonance are eliminated, or avoided.
  • the decoupler assembly 20 allows the belt driven accessory components 12 to temporarily operate at a higher speed or "overrun" the crankshaft 16 as the rotational speed of the crankshaft 16 changes with the speed of the engine 10, which results in smoother engine operation, less noise, and increased belt life.
  • the decoupler assembly 20 also dampens or isolates torsional vibrations experienced between the crankshaft 16 and the belt 18 during operation of the engine 10.
  • the decoupler assembly 20 is described above as part of an internal combustion engine, it should be appreciated that the decoupler assembly 20 can be implemented in any rotary or pulley-type belt drive system, such as a generator or a conveyer belt system, or in any system of rigid shafts with pulley or misalignment couplings where a hub load is not necessarily applied.
  • the output pulley 22 can be adapted to accommodate any type of drive element, such as a plastic or rubber multi-rib belt, a "V" belt, or a synchronous belt.
  • the output pulley 22 can also be adapted to accommodate other drive elements such as a steel flat belt, as used in a continuously variable transmission, for example, or a multi-link chain made of plastic or steel.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Pulleys (AREA)
  • Mechanical Operated Clutches (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Claims (20)

  1. Entkoppleranordnung (20), die umfasst
    eine Nabe (40) mit einer Drehachse;
    ein Antriebselement (22), das zur Drehung um die Drehachse um die Nabe (40) herum angeordnet ist, wobei das Antriebselement (22) eine innere Kupplungsfläche (26) hat; und eine Kupplung, die die Nabe (40) und das Antriebselement (22) koppelt,
    wobei die Kupplung eine Federschale (70, 100), eine Vielzahl von Bogenfedern (130) und eine Schlingfeder (140) umfasst, die Bogenfedern (130) an der Federschale (70, 100) angebracht und so eingerichtet sind, dass sie Drehkraft zwischen der Federschale (70, 100) und der Nabe (40) übertragen, die Schlingfeder (140) ein vorn liegendes Ende (144) sowie eine Vielzahl spiralförmiger Windungen (142) enthält und das vorn liegende Ende (144) antreibend mit der Federschale (70, 100) gekoppelt ist, wobei die spiralförmigen Windungen (142) mit der inneren Kupplungsfläche (26) des Antriebselementes (22) in Eingriff sind, dadurch gekennzeichnet, dass die Federschale (70, 100) zwischen der Nabe (40) und dem Antriebselement (22) aufgenommen ist,
    und, dass ein Abschnitt der spiralförmigen Windungen (142) der Schlingfeder (140) um einen Rand eines Abschnitts der Federschale (70, 100) herum gewickelt ist, wobei der Abschnitt der Spiralfedern (142) zwischen der inneren Kupplungsfläche (26) und dem Abschnitt der Federschale (70, 100) angeordnet ist und die Bogenfedern (130) im Inneren der Federschale (70, 100) so angeordnet sind, dass sie entlang der Drehachse axial vollständig zwischen einander gegenüberliegenden axialen Enden der Schlingfeder (140) positioniert sind.
  2. Entkoppleranordnung (20) nach Anspruch 1, wobei die Bogenfedern (130) Druckfedern sind.
  3. Entkoppleranordnung (20) nach einem der vorangehenden Ansprüche, wobei die Federschale (70, 100) ein Paar Gehäuseschalen umfasst, zwischen denen die Bogenfedern (130) aufgenommen sind.
  4. Entkoppleranordnung (20) nach Anspruch 3, wobei jede der Gehäuseschalen (70, 100) eine zylindrische Innenfläche (72, 102), die die Nabe (140) drehbar aufnimmt, und eine zylindrische Außenfläche (74, 104) enthält, die konzentrisch in die Schlingfeder (140) eingesetzt ist.
  5. Entkoppleranordnung (20) nach Anspruch 3 oder 4, wobei ein Führungsschlitz (82) in eine der Gehäuseschalen hinein geformt ist und das vorn liegende Ende (144) der Schlingfeder (140) in dem Führungsschlitz (82) aufgenommen ist.
  6. Entkoppleranordnung (20) nach Anspruch 5, wobei zumindest eine der Gehäuseschalen (70, 100) einen Gegengewichtsblock (98, 126) enthält, der zwischen der inneren (72, 102) und der äußeren Fläche (74, 104) dem Führungsschlitz (82) radial gegenüberliegend ausgebildet ist, um die Drehung der Federschale (70, 100) zu stabilisieren.
  7. Entkoppleranordnung (20) nach einem der Ansprüche 3 bis 6, wobei die Nabe (40) einen Hauptkörper (42), der so eingerichtet ist, dass er fest an einer Antriebswelle (16) angebracht ist, sowie einen zylindrischen Rand enthält, der sich radial von dem Hauptkörper (42) erstreckt und von den inneren Flächen (72, 102) zwischen den Gehäuseschalen (70, 100) aufgenommen wird.
  8. Entkoppleranordnung (20) nach einem der vorangehenden Ansprüche, die des Weiteren ein Schmiermaterial umfasst, das zwischen der Federschale (70, 100) und den Bogenfedern (130) angeordnet ist, wobei das Schmiermaterial wahlweise Fett oder Öl aufweist.
  9. Entkoppleranordnung (20) nach einem der vorangehenden Ansprüche, wobei die Kupplung des Weiteren einen Rand (75) umfasst, an dem eine erste der Vielzahl von Windungen (142) an das vorn liegende Ende (144) angrenzend anliegt, und der Rand (75) fest mit der Federschale (70, 100) verbunden ist.
  10. Entkoppleranordnung (20) nach Anspruch 9, wobei der Rand (75) so eingerichtet ist, dass er an wenigstens zwei Stellen an der Schlingfeder (140) anliegt.
  11. Entkoppleranordnung (20) nach Anspruch 10, wobei der Rand (75) eine spiralförmige Kontur hat.
  12. Entkoppleranordnung (20) nach Anspruch 9, wobei der Rand (75) so eingerichtet ist, dass er beim Betrieb der Entkoppleranordnung (20) in Reibeingriff mit der inneren Kupplungsfläche (26) ist.
  13. Entkoppleranordnung (20) nach einem der vorangehenden Ansprüche, wobei das Trägerelement eine Aussparung (84) aufweist, ein Einsatz (85) in der Aussparung (84) aufgenommen ist und der Einsatz (85) an einer Endfläche des vorn liegenden Endes (144) der Schlingfeder (140) anliegt.
  14. Entkoppleranordnung (20) nach einem der vorangehenden Ansprüche, wobei die Federschale (70, 100) eine Vielzahl separater bogenförmiger Vertiefungen (76) aufweist, in denen die Bogenfedern (130) einzeln aufgenommen sind.
  15. Entkoppleranordnung (20) nach einem der vorangehenden Ansprüche, wobei die Nabe (40) eine Vielzahl sich radial erstreckender Laschen (48, 50) umfasst und jede der Laschen (48, 50) eine Vorderkante (52) hat, die an einer entsprechenden der Bogenfedern (130) anliegt.
  16. Entkoppleranordnung (20) nach Anspruch 15, wobei die sich radial erstreckenden Laschen (48, 50) der Nabe (40) eine Hinterkante (54) umfassen, ein nicht metallischer Puffer (112, 114) mit der Federschale (70, 100) gekoppelt ist und Kontakt zwischen einer der Hinterkanten (54) und dem nicht metallischen Puffer (112, 114) relative Drehung der Federschale (70, 100) und der Nabe (40) zueinander in einer vorgegebenen Drehrichtung begrenzt.
  17. Entkoppleranordnung (20) nach Anspruch 16, wobei der nicht metallische Puffer (112, 114) integral mit einem Abschnitt der Federschale (70, 100) ausgebildet ist.
  18. Entkoppleranordnung (20) nach einem der vorangehenden Ansprüche, wobei das Antriebselement (22) eine Riemenscheibe ist.
  19. Entkoppleranordnung (20) nach Anspruch 18, wobei das Antriebselement (22) eine ringförmige äußere Bahn (24), die konzentrisch zu der inneren Kupplungsfläche (20) ist und so eingerichtet ist, dass sie einen Riemen (18) aufnimmt, eine Stirnplatte (28), die die äußere Bahn (24) und die innere Kupplungsfläche (20) aufnimmt, sowie einen zylindrischen Nabenabschnitt (30) enthält, der axial von der Mitte der Stirnplatte vorsteht und eine Naben-Lagerfläche (32) definiert.
  20. Entkoppleranordnung (20) nach Anspruch 19, wobei die Nabe (40) einen zylindrischen Lagerzapfen (46) enthält, der sich axial von der Mitte des Hauptkörpers (42) der Nabe (40) erstreckt und in die zylindrische Nabe (30) des Antriebselementes (22) eingesetzt ist.
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US20070037644A1 (en) 2007-02-15
JP2007506056A (ja) 2007-03-15
PL2273144T3 (pl) 2013-04-30
EP1668267A4 (de) 2008-03-05
BRPI0414587A (pt) 2006-11-07
PL1668267T3 (pl) 2013-03-29
US20100032258A1 (en) 2010-02-11
CA2539790C (en) 2013-06-25
KR20060088541A (ko) 2006-08-04
EP1668267B1 (de) 2012-10-31
WO2005028899A1 (en) 2005-03-31
CA2539790A1 (en) 2005-03-31
EP2273144A1 (de) 2011-01-12
US7954613B2 (en) 2011-06-07
CN100513816C (zh) 2009-07-15
US7624852B2 (en) 2009-12-01
EP1668267A1 (de) 2006-06-14
CN1856664A (zh) 2006-11-01
KR101134785B1 (ko) 2012-04-13

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